Live collar assembly for winding machines



April4, 1967 T. M. OWENS 3,312,408. 7

LIVE COLLAR ASSEMBLY FOR WINDING MACHINES Filed Oct. 12, 1964 2Sheets-Sheet 1 WWI INVENTOR.

THOMAS M. OWENS Ewen- Q 26 lBb PRIOR ART April 4, 1967 T. M. OWENS LIVECOLLAfi ASSEMBLY FOR WINDING MACHINES 2 Sheets-Sheet 2 Filed Oct. 12,1964 I INVENTOR.

THOMAS M. OWENS x N E h a m. EU .1 \%F% k BMM United States PatentOfifice 3 ,3 12,408 Patented Apr. 4, 1967 3,312,408 LIVE COLLAR ASSEMBLYFOR WINDING MACHINES Thomas M. Owens, Wanakena, N.Y. 13695 Filed Oct.12, 1964, Ser. No. 403,317 1 Claim. (Cl. 242-66) This invention relatesto high speed winding machines, and more particularly to the type ofmachine having a pair of winding drums for driving and supporting theroll of material wound and a removable aligning shaft which isdisplaceable with respect to the drums for guiding the roll during thewinding process.

In the manufacture of paper, particularly high quality paper having acoated surface, a tubular metal core, on which the paper is wound, isemployed in the various coating processes. With recent improvements inpaper making, higher speeds are required and longer and heavier rollsare used.

In winders particularly, modern processes require speeds twice that ofother machines so that the winding process can be completed insufficient time for the operator to remove the wound rolls and install anew core, to adjust slitters and cutters, and to do all the other workrequired between runs. When other machines are run at speeds up to 2,000feet per minute, a winder must be capable of speeds up to 4,000 feet perminute. When rolls as long as twelve feet are wound, the weight of thecompleted roll may be as much as 2 tons, requiring more time, as well asequipment, to handle.

' Older winding machines, although equipped to handle the larger rolls,rarely can be run at speeds as high as 1,500 feet per minute.

One of the primary objects of the present invention, accordingly, is toprovide means for adapting older winding machines for satisfactoryoperation at higher speeds as well as means in new machines adaptingthem for high-speed operation. Another important object is to providemeans for the elimination of vibration when such machines are run athigh speeds.

-. A further object is to cut the time required for unloading themachine after the roll is wound.

A still further object is to reduce the frequency of necessary repairssuch as replacement of bearings.

Other objects and advantages will be apparent from the followingdescription taken in conjunction with the accompanying drawings, inwhich:

FIGURE 1 is a fragmentary perspective and diagrammatic view of a windingmachine in which the device of the invention may be installed; 1

FIGURE 2 is a fragmentary longitudinal sectional view of one end of thewinding shaft of the machine of FIGURE 1 showing the collar usuallyemployed to mount the core on the shaft;

FIGURE 3 is a fragmentary longitudinal sectional view of a winding shaftshowing the live collar assemblies according to the invention at eitherend of the shaft, the assembly at one end being shown rotated 90 fromthat at the other end;

FIGURES 4 and 5 are end views of a collar assembly as viewed in thedirection of the arrows 4-4 and 55, respectively, of FIGURE 3; and

FIGURE 6 is a greatly enlarged sectional view of the collar member andcore at one end of the shaft of FIG- URE 3.

Referring particularly to FIGURE 1, the winding machine 10 includes twowinding drums 11 and 12 supported side-by-side in suitable bearings onthe frame 13 of the machine. The drums are driven, by means not shown,to rotate in the same direction as indicated by the arrows in FIGURE 1.The paper 14 is wound into rolls 15 on a tubular metal core 16 mountedcoaxially on a winding shaft 17 by means of collars 18 at either end ofthe core.

The winding drums are mounted on parallel axes and are spaced apart asufficient distance to feed the web of paper 14 up between the drums tothe core 16 on which it is wound. Slitters and cutters for cutting theweb into narrower widths and for cutting the web at the end of the rollsmay be mounted beneath the drums.

' Shaft 17 is displaceable upward as the web 14 is wound on the rolls15, and is held in parallel relation with the axes of the drums 11, 12by means of verctically extending guide tracks 20 at either end of theshaft. One of two slides of carriers 21 is shown at one end of shaft 17.The slides 21 are slidably mounted on the tracks 20, 20 and carrybearing means 22 for the shaft 17.

At least one of the bearings 22 is of the split-boX-type and shaft 17can be withdrawn from the core 16 when the rolls 15 have been wound sothat the rolls on core 16 can be removed from the machine. The bearing22, shown in FIGURE 1, has a cover or top portion 22 normally held inplace by the latch 23, but which may be swung up and away from thebottom portion on the hinge 22b when the latch is released. Thrust rings24 may be removably secured on shaft 17 on either side of the bearing 22to prevent end play of the shaft during the winding operation.

A top-pressure or rider roll 25 is usually provided on top of the rolls15 to give the latter a downward pressure on drums 11, 12 before thepaper rolls have attained sufficient weight to have proper frictionalengagement with the drums. Means for lessening the pressure of the riderroll as the weight of rolls 15 builds up is usually provided in themeans, not shown, which secure roll 25 in the guide tracks 20.

In FIGURE 2 is shown the conventional means for securing the core 16 onshaft 17. A collar 18 has a slide fit on the shaft 17 and has a reducedportion 18a having a slide fit within the end of core 16. A shoulder 18bis adapted to abut against the end of core 16 when a collar is securedat each end of the core to shaft 17 by means of a setscrew 26.

It has been found that, aside from scarring the shaft 17, the set screws26 cause an offsetting or drawing away of the axis of core 16 from itscoaxial relation with the shaft as is exaggeratedly indicated in FIGURE2. While this offsetting may not be noticeable at slower speeds, itcauses excessive vibration when the winder is run at speeds exceeding1500 feet per minute.

Furthermore, the split bearing 22 has been found to be unsuited for useat higher speeds in that it becomes worn and must be replaced atfrequent intervals.

FIGURES 3-6 illustrate the live collar construction of the presentinvention which has been found to overcome the foregoing disadvantages.A new winder shaft 27 is provided for the machine 10 and the bearings 22are replaced with new ones, if worn. Shaft 27 may have reduced ends toprovide a shoulder 28 at either end for abutting against the bearings 22to prevent end play without the need for thrust rings 24. To cut costsand to lighten the shaft, the latter is preferably provided with solidend portions 27a, and a tubular part 2717 connecting the end portionsand comprising the major portion of the shaft. Annular rings 27c, weldedor otherwise secured to the end portions 27a and tubular portion 27b,are employed to-secure the portions of the shaft 27together.

A live collar assembly 30 is provided at either'end of core 16 and eachassembly includes a collar member 31 which is frictionally engagedcoaxially within the end of the core 16. Member 31 has a radiallyprojecting flange 32 at the end of the core for securing the coreendwise of the shaft 27.

As' best seen in FIGURE 6, the inner end of member 31 has an inwardlytapered end 31a for facilitating its insertion within the end of thecore. The remainder 31b of the portion inserted within the core 16 isgiven a carefully machined sliding fit with the inner wall of the coreend, which is also carefully machined. To assure good frictionalengagement of the member 31 with core 16, the outer end of portion 31bis given a very slight outward taper exaggeratedly shown at 31c inFIGURE 6.

The inside of the member 31 has an undercut recess, or enlarged insidediameter, at 33 and the outer race 34a of a ball or other rolling-membertype bearing assembly 34 is pressed into the recess 33 so as to befirmly secured in the recess. No portion of the collar member 31 engagesthe shaft 27.

The inner race 34b of the bearing assembly 34 has a sliding fit with theend portion 27a of the winding shaft and is Wider than the upper race,having an annular portion 340 extending axially outward beyond thecollar member 31.

Also outward of the member 31, a split-ring annular clamp 35 has its twosemi-circular halves adjustably secured together by the screws 36, asshown, so as to be removably secured to the end portion 27a of the shaft27. Clamp 35 has an annular portion 35a, also split, projecting towardthe member 31 and undercut to loosely overlie the projecting portion 340of the inner bearing race 34b.

As best seen at the right hand end of FIGURE 3 a pair of pins 37,carried in clamp member 35 midway between screws 36, have a drive fit indiametrically opposite, axially aligned holes in the clamp portion 3511which overlies the inner race portion 340. Pins 37 project inwardly andhave a slide fit in appropriate holes in the inner race member so thatthe clamp 35, bearing assembly 34 and collar 31 become a unitaryassembly with the collar being rotatable relative to the clamp and innerrace 340, see FIGURES'4 and 5.

In operation, a new core 16 is placed in position on top of drums 11 and12 after any wound rolls have been removed. Shaft 27 is inserted in thecore and the live collar assemblies 39 are slid onto the shaft at eitherend of the core. The outer ends of shaft 27 are then secured in bearings22 in conventional manner. However, since bearings 34 form a part of thecollar assemblies 30, a pin 40 may be passed through bearing 22 andshaft 27, as indicated in broken lines in FIGURE 1, to prevent shaft 27from rotating.

The assemblies 30 are then inserted with their collar members 31 withinthe ends of core 16. The tapered ends 31a of the collar membersfacilitate their insertion and the taper at 31c is so slight that theflanges 33 can be forced up against the ends of core 16 as shown in FIG-URE 3.

The screws 36 are then tightened to clamp the assemblies 30 in position.The paper 14 is then started around the core 16 and the winder isstarted in the usual manner.

It has been found that,-since the shaft 27 does not rotate, less massmust be put in motion and higher speeds may be more quickly reached.Moreover, the decreased bearing friction provided by the roller memberbearings 34, as compared to the older type bearings 22, permits thewinder core 16 to be rotated by the drums 11, 12 at high speeds before aheavy load of paper wound thereon is built up and the rider roll 25 neednot be employed. It has also been found that the ball bearings 34provide such lowfriction, regardless of load or speed, that the pin 40,to keep shaft 27 from rotating, may be dispensed with as unnecessary.

The collar portion 31 is self-centering when it is insorted in the core16 so that there is no offsetting of the core axis from the axis ofrotation as is the case when the setscrew-clamped collar 18 is used.Moreover, there isno scarring of the shaft 27 when the clamps 35 aretightened. The halves of each split ring clamp 35 have extensive surfacecontact with shaft 27 when the screws 35 are tightened and, since thepins 37 extend parallel to the screws 36, there is no distortion of theinner race 34b.

Since the shaft 27 does not rotate, there is less mass to rotate andfewer parts to cause imbalance and hence vibration. Furthermore, anysagging or deflection of the shaft, however slight, has little effect onthe rotating core, collar member and outer race which are supported onlyat the two ends of the shaft. The bearings 22 are used only as clamps tosecure the ends of shaft 27 on the slides 21 and hence do not requirereplacement or renewal. Since bearings 34 can be replaced by simplysupplying new assemblies 31) for the machine, work stoppages to renewbearings are eliminated. Wear due to end play or thrust in the ballbearings, 34 are minimal in contrast to that in older, split-typebearings 22. Nevertheless, shaft 27 does extend across the machine togive a rigidity to the rollaligning mechanism which would be impossibleif only stub-shafts were used.

When the rolls 15 are built up on core 16, the machine is stopped, paperweb 14 is cut and the core and rolls removed from the machine asfollows: The split bearing 22 shown in FIGURE 1 is opened and carrier 21lowered out of the way. The clamp 35 at the far end of the machine inFIGURE 1 is then loosened by simply backing off one of the screws 36 aquarter turn. The collar member of the live collar assembly 36 at thenear end shown in FIGURE 1 is easily dislodged from engagement with theends of core 16 by striking the protruding far end of shaft 27 with arawhide or rubber hammer.

Shaft 27 is then withdrawn from the core 16 without loosening the clamp35 of the near assembly 30 and the paper rolls on the core 16 may thenbe rolled, or otherwise removed from their position on the winding drums11, 12. The assembly 30 at the far end is removed from the core in anyconvenient manner. When another core 16 is installed for the nextoperation of the machine, this live collar assembly 30 at the far end ofthe machine is the only one which has to be replaced on shaft 27.

The preferred construction of shaft 27, using the tubular portion 27bfor the major length of the shaft, shown in FIGURE 3, provides means forlightening the weight of the shaft, which is usually manually installedand withdrawn, without sacrificing rigidity.

As will be apparent to those familiar with the art, the invention may beembodied in other specific forms without departing from the spirit oressential characteristics thereof, The embodiment disclosed is thereforeto be considered in all respects as illustrative rather thanrestrictive, the scope of the invention being indicated by the appendedclaim.

What is claimed isz A high speed paper winding machine having a tubularcore on which the paper is wound and a pair of rotatably driven windingdrums for supporting the core and the paper thereon, a non-rotatingshaft displaceable upward With respect to the drums; guide means at eachend of the shaft for maintaining the shaft in alignment with the drums,the shaft being removably secured to the guide means; and a collarassembly at each end of the core securing the core coaxially on theshaft; each assembly including a collar member having a tubular portionfrictionally and removably engaged coaxially within the core and havinga radially-projecting thrust-resisting portion at the end of the core,and rolling member type bearing means having an outer race membersecured coaxially within the collar member and having an inner racemember slidably and coaxially mounted on the shaft, the inner racemember having an annular portion projecting axially and externally ofthe collar member, a pair of semicircular clamp members forming a splitannular ring about the shaft, screw means extending on either side ofthe shaft at a right angle to the shaft securing the clamp memberstogether and removably securing them to the shaft, each clamp memberhaving a portion overlying the projecting portion of the inner race, andpin means disposed radially on either side of the shaft and extending ina direction at a right angle to that of the screw means and pivotallysecuring the inner race member to the clamp members.

References Cited by the Examiner UNITED STATES PATENTS 1,821,877 9/1931Bowne 308236 6 2,613,881 10/1952 Kottmann 24268.4 2,665,930 1/1954Stanley 308236 X 3,079,101 2/ 1963 Rockstrom 24266 FOREIGN PATENTS 736,537 9/ 1955 Great Britain.

FRANK J. COHEN, Primary Examiner.

STANLEY N. GILBREATH, Examiner.

2,148,065 2/ 1939 Farmer 24268.4 10 W. S. BURDEN, Assistant Examiner.

